Valve assemblies

ABSTRACT

A valve assembly for controlling the flow of fluids such as liquid sodium at high temperature comprises a body having internal separate inlet and outlet chambers surrounded by an annular plenum chamber and fixed ports providing fluid communication between the plenum chamber and the respective inlet and outlet chambers. Rotary or slidable valve members are shiftable for controlling fluid flow through the chambers. A rotatable actuating shaft is operably connected to the shiftable valve member and it projects out of the valve body into an enclosing housing containing a thermally sensitive freeze seal means and mounting a heat radiating device.

United States Patent Bake et a]. [4 1 Aug. 22, 1972 54] VALVE ASSEMBLIES 2,410,960 11/1946 Bunn ..137/338 x 72 I t 2 A I Simmons m. X 1 ms dm B. 3,267,945 8/1966 Bottoms ..2s1/344 x Andrew Mask Bemm 3,356,809 12/1967 Colclaser, Jr. et al.325l/347X leville, both of OHara Township; John Hyde Fowler, Shaler Township, all of Pa.

[73] Assignee: Rockwell Manufacturing Company,

Pittsburgh, Pa.

[22] Filed: March 20, 1970 [21] Appl. No.: 21,264

[52] U.S. Cl. ..137/338, 251/344 [51] Int. Cl ..Fl6k 49/00 [58] Field of Search ..251/340, 344, 345, 346, 347, 251/348; 137/338 [5 6] References Cited UNITED STATES PATENTS 3,005,468 10/1961 Erwin et a1 ..251/344 X 3,135,293 6/1964 Hulsey ..251/345 X 3,485,263 12/1969 Laux ..251/344 X 3,148,859 9/1964 Sevetz ..137/338 3,374,985 3/1968 Gessic ..251/347 X 2,845,306 7/1958 Carver ..137/338 X FOREIGN PATENTS OR APPLICATIONS 1,190,161 3/1959 France ..251/340 Primary Examiner-Sarnuel Scott Attomey-Strauch, Nolan, Neale, Nies 8L Kurz [57] ABSTRACT A valve assembly for controlling the flow of fluids such as liquid sodium at'high temperature comprises a body having internal separate inlet and outlet chambers surrounded by an annular plenum chamber and fixed ports providing fluid communication between the plenum chamber and the respective inlet and outlet chambers. Rotary or slidable valve members are shiftable for controlling fluid flow through the chambers. A rotatable actuating shaft is operably connected to the shiftable valve member and it projects out of the valve body into an enclosing housing containing a thermally sensitive freeze seal means and mounting a heat radiating device.

15 Claims,'1l Drawing Figures Patented Aug. 22, 1972 8 Sheets-Sheet l Inventors EARL ALLAN BAKE,

ELDERT B. POOL, ANDREW HANKOSKY, BERTRAM J. MILLLVILLE, d JOHN HYDE FOWLER ATTORNEYS Patellnted Aug. 22, 1972 3,685,536

8 Sheets-Sheet 2 Inventors Q EARL ALLAN BAKE, ELDERT B. POOL, ANDREW HANKOSKY, BERTRAM J. MILLEVILLE and JOHN HYDE FOWLER AT TORNEKS Patented Aug. 22, 1972 3,685,536

' 8 Sheets-Sheet S Inventors EARL ALLAN BAKE,

ELDERT B. POOL, ANDREW HANKOSKY, BERTRAM J. MILLhVILLE and JOHN HYDE FOWLER ATTORNEYS Patented Aug. 22, 1972 8 Sheets-Sheet 4 Inventors EARL ALLAN BAKE, LLDERT B. POOL, ANDREW HANKOSKY, BBR'I'RAM J. MILLEVILLE and JOHN HYDE FOWLER Patented Aug. 22, 1972 8 Sheets-Sheet 6 Inventors EARL ALLAN BAKE,

ELDERT B. POOL,

ANDREW HANKOSKY, BERTRAM J. MILLEVILLE and JOHN HYDE FOWLER A T TOR/V5 Y5 Patented Aug. 22, 1972 8 Sheets-Sheet 6 k GE I nventors EARL ALLAN BAKE,

ELDLRT B. POOL,

ANDREW HANKOSKY, BERTRAM J. MILLEVILLE and JOHN HYDE FOWLER /WWW Wd/QM ATTORNEYS Patented Aug. 22, 1972 3,685,536

8 Sheets-Sheet 7 Inventors EARL ALLAN BAKE, ELDERT B POOL,

ANDREW HANKOSKY, BERTRAM J. MILLEVILLE and JOHN HYDE FOWLER ATTORNEYS VALVE ASSEMBLIES The invention described herein was made in the course of a contract with the US. Atomic Energy Com- This invention relates to valve assemblies for controlling the flow of materials such as liquid sodium in the range between its melting point (about 97.5 C.) and its boiling point (about 880 C.

The invention in its preferred embodiments is directed to valve assemblies for use in liquid sodium systems. The severe operating conditions required by such systems combined with the need for reliable total separation of liquid sodium from the valve environment creates serious problems which conventional types of valves cannot accommodate and which such conventional valves may not be made capable of accommodating because of configuration and performance limitations inherent in known designs.

Most conventional valves employ massive metal sections to provide strength required to sustain ordinary pressures and mechanical loadings. Bulk strength may be required for stress limitations or, as in the case of most large plug valves, to provide the rigidity necessary for functional performance. Such massive sections are undesirable in valves for high temperature sodium service because of thermal gradients which create stress problems, and, in the case of non-uniform sections, may cause distortion resulting in the loss of functional geometry due to different average section temperatures. These problems would be particularly acute in large valves.

A major object of the invention is to provide a valve assembly structure utilizing component parts which inherently provide for minimum acceptable uniform wall thickness. This is desirably accommodated through the use of formed plates or sheets and cylindrical and related components assembled as by welding. This approach also facilitates the use of well proven techniques for rigorous stress analysis.

Another object of the invention is to provide a valve structure that is symmetrical about the center line or flow axis of the pipe system in which it is installed. Such provides many benefits. General thermal distortion can be minimized, and theoretical stress analysis is greatly simplified and made more accurate and dependable. Symmetry provides maximum mechanical strength with a minimum of structural material. Symmetry also permits maximum use of the most readily produced shapes of structural materials and, in addition, hydrostatic and hydro-dynamic forces can be totally or nearly balanced.

A further object of the invention is to provide valve assembly structures wherein the mechanical energy required to operate the control member is delivered through the pressure boundary to moving valving members by rotation in specially constructed seals.

Still a further object of the invention is to provide a novel valve assembly employing at least one movable valve member, the movement of which is controlled by special linkage activated by a rotary shaft which extends to the exterior of the valve assembly through a novel freeze seal assembly.

Still a further object of the invention is to provide a valve assembly which takes advantage to the maximum practical degree of a uniform ratio between sodiumwetted surface area and local metal volume of the valve structure. This tends to avoid gross differences between the rates of thermal expansion and contraction between various parts of the valve structure. If this ratio is maintained substantially uniform, the average temperature of the various metal sections should rise and fall at similar rates, and this minimizes thermal stresses and distortion.

A still further object of the invention is to provide a valve structure which minimizes cavitation, particularly in valve assemblies used for absorbing fluid energy. Cavitation is a problem which results when flowing liquid is subjected to a decrease in pressure followed by an increase in pressure as occurs when the liquid flows past an orifice in the conduit. When the liquid is subjected to a decrease in pressure, it boils and forms bubbles or voids which later collapse as the pressure recovers and creates shock waves which tend to deteriorate the internal surfaces of a valve over a period of time. The amount of such damage depends upon the number of bubbles and their proximity to the internal surfaces of a valve.

Cavitation is minimized in the valve assembly of the invention by minimizing recovery of static pressure after it has been converted into velocity pressure in an orifice. This is actually achieved in the invention by permitting the liquid discharged through an orifice to flow into a natural plenum filled with the liquid. The liquid filled plenum tends to dissipate the high velocity without a recovery of static pressure. For a given energy dissipation, the minimum pressure is not so low, so that less boiling occurs and therefore, there is less cavitation. Cavitation, which may occur, occurs away from the walls thereby minimizing damage to the valve.

Certain embodiments to be described actually provide for two-state (multi-stage) orifice discharge arrangements wherein liquid in the inlet chamber of a valve is discharged through one set of orifices to a relatively large plenum which surrounds the throttle mechanism, and then is discharged from the plenum through a second set of orifices into the outlet chamber of the valve (a second plenum). With each stage made as cavitation resistant as possible, the minimum number of stages are required for given fluid power absorption. The alternate out and in flow through adjacent stages minimizes liquid sodium volume, extremely important in a test facility where thermal shock testing is to be performed, and it also conserves on sodium inventory.

In the various embodiments herein both rotary and longitudinally slidable valve members will be disclosed, as well as single and multi-stage valving. Novel thermal seal arrangement for shafts actuating the valve members will also be disclosed.

BRIEF DESCRIPTION OF DRAWINGS FIG. 1 is a generally perspective side elevation partially broken away and in section showing a valve assembly incorporating the invention according to a preferred embodiment;

FIG. 2 is a mainly sectional elevation showing details of the valve assembly of FIG. 1;

FIG. 3 is an enlarged partial view in section showing further detail;

FIG. 4 is a transverse section substantially on line 4- 4 in FIG. 2;

1 FIG. 6 is a generally perspective view partially broken away and in section showing a further embodiment; I

FIG. 7 is an enlarged fragmentary section showing the slidable valve sleeve and operating linkage of FIG. 6;

FIG. 8 is a section substantially on line 8-8 of FIG.

FIG. 9 is a top plan fragmentary view partly broken away and in section showing detail of the operating linkage of FIG. 6-8 substantially as viewed on line 9--9 in FIG. 7 and and FIG. 10; g

' FIG. 10 is an elevation in section illustrating a further embodiment related to FIGS. 6-9 but wherein two slidable valve elements are employed; and

FIG. 11 is a fragmentary view partly sectioned showing another two stage control embodiment PREFERRED EMBODIMENTS The valve assembly 20 of FIGS. 1-5 comprises a body 21 having a spherical shell 22 .disposed between respective inlet and outlet conduits 23 and 24.

.In one mode of fabrication, as shown in FIG. 2, conduits 23 and 24 are formed with identical generally conical flared open inner ends 25 and 26 that terminate adjacent the periphery of body shell 22, and'these ends are bridged by a rigid cylindrical sleeve 27 that is welded to the conduits at opposite. ends in circular regions indicated at 28 and 29.

Sleeve 27 thereby rigidly and permanently joins the open ends of conduits 23 and 24, and as shown sleeve 27 extends through diametrically opposite openings in shell 22 where annular weld regions 31 and 32 join ing an essential continuation of the outlet conduit.

Sleeve 27 defines with the interior of shell 22 an annular plenum chamber 38 extending circumferentially around sleeve 27.

A moveable valve member in the form of a sleeve 41 disposed in plenum chamber is rotatably mounted upon and about the axis of sleeve 27. As shown in FIG. 2, sleeve 41 is axially confined at opposite ends by retainer rings 42 and 43 secured to sleeve 27 with annular thrust bearings 44 and 45 interposed between the flat'parallel ends of sleeve 41 and the retainer rings.

Sleeves 27 and 41 have cooperating setsof flow control ports or apertures that coact to regulate fluid communication between inlet space 36, plenum chamber 38 and outlet space 37. Preferably the ports on one sleevev are of a rectangular shape and those on the other sleeveare contoured as will appear.

In the illustrated embodiment, fixed sleeve 27- is formed with four equally circumferentially spaced inlet ports 46 opening from inlet space 36, and with four equally spaced outlet ports 47 opening to outlet space 37. Similarly rotatable sleeve 41 is formed. with four equally circumferentially spaced ports 48 sized and located for coaction with inlet ports 46, and four equally circumferentially spaced ports 49 sized and located for coaction with outlet ports 47 Sleeve 27 is shown inrotated valve closed position in FIG. 1 wherein all of ports 46 are covered byportions of sleeve 41 extending circumferentially between ports '48, and all of ports 47 are covered by portions of sleeve 41 extending between ports 49. In this condition plenum chamber 38 is isolated from both the inlet and outlet.

In the disclosed embodiment, all of fixed ports 46 are of generally keystone shape but with the symmetrical sides contoured to characterize the opening. Each is oriented in the same direction and are of the same size..

The cooperating rotatable sleeve ports 48 are preferably rectangular, each having the same circumferential dimension as a port and a longitudinal dimension equal to the maximum {longitudinal dimension of a port 46, as indicated in dotted lines in FIG. 2.

All of the fixed ports 47 are similarily shaped and oriented in the same direction and are of the same size. The cooperating ports 49 of the rotatable sleeve are preferably-rectangular each having the same circumferential dimension as a port47' and a longitudinal I dimension equal to the maximum longitudinal dimension of a port 47 as indicated in dotted lines in FIG. 2.

It will benoted that coacting inlet ports 46 and 48 are of smaller area than coacting outlet ports 47 and various coacting ports may be selected for desired control sequences.

Three annularbearing and seal regions 51, 52 and 53 are provided between the relatively rotatable contacting surfaces of sleeves 27 and 41. Each such'seal region may comprise, see FIG. 3, a shallow annular groove 54 in sleeve 41 containing an inlaid smoothbearing surface element 55 of hard or hardened metal cooperating with a split piston ring type annulus 56 mounted in an annular groove 57 in sleeve 27. Region 52 is located longitudinally between the sets of ports, and regions 51 and 53 are located at the opposite sides of the sets of In each .of these regions the fixed inlay 55 may be replaced by a relatively loosely mounted flat ring held against rotation as by a suitable pin. This permits relative shift of the ring during thermal changes while eliminating localized stresses.

Mechanism is provided for controllably rotating sleeve 41, andthis comprises two apart devices 61 and 62. These devices are identical, and one is shown in enlarged detail in FIG. 3. Referring .to FIG. 6, shell 22 has an opening 63 through which extends a valve operator shaft 64. that is .shaft 64, and axial shift of lever-68 on the shaft is limited by boss 66 and a retainer ring 72 fixed on the shaft. A retainer ring 70 is secured to shaft 64 at the other side of boss 66 and a flange of radial bearing 65 extends to provide a thrust bearing between boss 66 and ring 70. Similarly thrust bearings are provided between the ends of hub 69 and ring 72 and boss 66.

Shaft 64 has an elongated bore 60 in its inner end for a purpose to appear. Lever 68 (see FIG. 4) is provided at its other end with a pivot 73 on which is rotatably mounted one end of a double arm link 74. The other end of link 74 is pivotally connected at 75 to a lug or projection 76 rigid with sleeve 41.

Where it emerges from shell 22, shaft 64 passes through a housing structure generally designated at 77. This housing structure comprises a hollow portion having a ring 79 fixed on one end and welded as at 81 to shell 22. The space around shaft 64 between shell 22 and ring 79 is sealed by surrounding arcuated shield 82 welded to both ring 79 and the shell.

Housing portion 78 has an end flange 83 secured to the end flange 84 of another housing portion 85, as by bolts 86, and these housing portions enclose the major portion of shaft 64 outside the shell 22.

Within the housing 77, shaft 64 extends through a packing annulus 87, a cylindrical thermal barrier sleeve 88, an annular packing 89, a coiled compression spring 91 and a chevron-type packing annulus 92. At its outer end housing portion 85 has a flange 93 to which is secured as by bolts 94 the flange 95 of an adjustable packing gland 96 engaging the outer end of packing 92.

A massive ring 97 of copper or like high heat conductive metal composed of two half rings, is brazed on housing 77. A plurality of heat dissipating rods 99 project generally radially from ring 97, and these rods have sheet metal heat radiation fins 101 secured thereon.

The outer end of shaft 64 extends into a motor 102 x which may be of the rotary piston compressed air operated type, which rotates shaft 64 during valve adjustment as desired. Suitable supply conduits and valving (not shown) are provided for reversible actuation of shaft 64 by Motor 102. Motor 102 is supported rigidly on housing 77 by a cage structure 103 fixed as by welding to ring 98, which is welded to housing 85.

Housing 77 has an opening 104 to which is connected a tube 105 connected to a supply source of inert gas diagrammatically indicated at 106. A filter or gas cleaner 107 is provided in tube 105 for cleaning gas entering housing 77 between the packings 89 and 92.

During operation the shafts 64 are rotated together in synchronism so as to exert balanced 180 apart forces turning sleeve 41 in either direction. When ports 48 and 49 are moved into overlap with ports 46 and 47 respectively this provides a controlled flow passageway through inlet chamber 36, plenum chamber 38 and the outlet or second plenum chamber 37. The amount of overlapping area between the ports 46 and 48 or ports 47 and 49 will determine the flow rate through the system which can be varied by rotating sleeve 41 to vary the amount of overlapping area between the control ports. Thus the overlapping areas between the respective ports serves as orifices with cross-sectional areas that can be varied by rotating sleeve 41.

With further reference to the ports 46, 47, 48 and 49 the contours of these apertures can be varied and characterized to optimize system performance. This characterization may be different for each stage to share the pressure drop so as to minimize cavitation. In FIG. 2 the contoured ports 46 and 47 are shaped to provide a known constant percentage rate fluid flow increase as the leading edge of a rectangular shaped port 48 and 49 traverses the circumferential length of the contoured ports. It should be noted that in both FIGS. 1-5 the first stage ports 46 and 48 are smaller than second stage ports 47 and 49 to provide staged pressure drop to equalize resistance to cavitation.

In the two stage control of FIGS. 1-5, the open valve provides a first measure of pressure drop as the liquid sodium enters plenum chamber 38 and then a further but lesser pressure drop as the liquid sodium leaves the plenum chamber and enters the outlet.

An arrangement of four inlet and four outlet ports as shown in each sleeve will provide a radially balanced structure and it is anticipated that such an arrangement may constitute the most practical configuration of ports. Each port should be provided in an arc length of less than 45 in order to provide sealing overlap with the adjacent sleeve in the off position. Altemately, the structure could utilize a larger number of ports requiring a lesser degree of rotation, or a smaller number of ports requiring greater rotation, as found suitable. However, it must be recognized that the possibility of leakage at the interface between the rotary sleeve4l and stationary sleeve 27 compromises low flow control and is proportional at the number of ports. The sleeve 41 is also axially balanced for differential pressure forces. The bearing loadings are therefore-minimized. The axially unbalanced pressure is carried by the fixed members in the assembly.

FIG. 3 illustrates best a preferred freeze seal structure for sealing each valve operator shaft 64 in a liquid sodium environment. This freeze seal described and shown in the drawings may be specifically directed to a shaft operated by rotary motion. Such a freeze seal offers the following advantages:

1. The freeze section may be short to minimize operating torque.

2. A blanket of inert gas, preferably provided with an adjacent getter" cannister is provided to minimize formation of undesirable sodium oxide which may tend to abrade and interfere with the desired operation of shaft 64.

3. The freeze seal prevents convective circulation of sodium between the main sodium stream and the temperature gradient zone, to minimize cold trapping at the freeze seal.

Shaft 64 which is supported internally of the shell 32 by a bearing at has a bore 60 within the part in plenum chamber 38. This minimizes the mass of the shaft permitting it to respond faster to temperature changes of sodium within shell 22. The major portion of shaft 64 externally of shell 22 is enclosed by the housing 77 containing the freeze seals.

The primary seal 89 preferably comprises a matrix of sodium and metal wool packing such as steel wool with the sodium present in its'solid form. Clearance between shaft 64, shell 22 and the tubular housing members are such as would permit liquid sodium to seep or flow to the freeze seal zone at 89. At this zone, tubular housing member has clamped to it the massive ring of copper 97 or some other metal having a high coefficient of heat transfer. Ring 97 serves as a heat sink to withdraw thermal energy from the sodium in this zone, thereby causing the sodium to solidify and seal the shaft 64. To further enhance the efficiency of heat sink ring Hot packing 87 (fine metal wool) and a thermal barrier 88 are provided intermediate retaining ring 79 and the primary freeze seal 89 to inhibit convective flow of liquid sodium and insulate the freeze seal from the high temperature of liquid sodium in the vicinity of body aperture 63. Thermal barrier 88 is a sleeve-type insert in housing 77 formed of a material having a relatively low coefficient of heat transfer such as a stainless steel ring provided with an annular void surrounding shaft Inert gas such as argon may be introduced by means of conduit 105 to the space occupied by spring 91 to prevent oxidation of the sodium seal 89. The formation of sodium oxide, a hard abrasive substance, in this structure would likely damage the surface of shaft 64 and thus be detrimental to the operation of the valve. The oxygen getter. cannister 107 is provided as a secondary protection measure in case the supply of inert gas fails. 1

FIGS. 6-10 disclose the invention in embodiments using slidable rather than rotatable valve elements.

Referring to FIGS. 6 and 7, the valve body is similar to that of FIGS. 1-5 in thatit comprises a spherical shell 22, outlet conduit 24 and an inlet conduit 23. In this embodiment the inlet conduit has a cylindrical exing a smooth cylindrical surface 125 in bearing engagement with the smooth cylindrical inner periphery 126 of conduit extension 110, and a front annular land 127 having a smooth cylindrical surface 128. in bearing engagement with the smooth cylindrical inner periphery 129 of sleeve 1 14.

At its front edge, sleeve 114 is formed with an annular flat smooth seating face 131 of uniform width adapted, in valve close position,' to engage the similar annular flat smooth fixed seating face 132 that is formed on an integral internal annular sleeve rib 133 in inlet chamber 116. Faces 131 and 132 engage in a plane normal to the valve axis. 7

Referring to FIG 7,. the movable valve sleeve forwardly of land 124 carriesan annular axially'compressible and expansible resilient seal ring 134 that in a i preferred form is of generally inverted U-shape in cross tension between the flared inner portion and (see welded'at 115, and the inner flared end of outlet conduit 26 where it is welded as in FIG. 2.

Sleeve 1 14, midway of its ends, is bridged by a fixed transverse closure wall" 33 welded thereto at and having a concave surface facing the inlet. Wall 33 separates thev interior of sleeve 114 into an inlet chamber 116 and an outlet chamber 117.

At the inlet side of wall 33, sleeve 1 14 is formed with a plurality of inlet ports 118 of the same size and shape preferably equally distributed circumferentially around the sleeve. Here four rectangular ports 1 18 are used. At the other side of wall 33 a plurality of outlet ports 119 of the same size and shape are formed in sleeve 114 and distributed equally circumferentially. Here four rectangular ports 1 19 are used. Ports 1 19 are preferably of at least the same or slightly larger area as compared to ports 1 18.

Shell 22 defines'with sleeve 114 a plenum chamber 121 circumferentially surrounding the sleeve and open to both the inlet ports 118 and outlet ports 119.

A movable valve member in the form of a slidable cylindrical sleeve 122 is shown in valve open position in FIG. 7, and its operating mechanism later to be described is indicated at 123.

Valve sleeve 122 is slidably supported for reciprocasection with one leg backed by land 124 and the other leg carrying an annular uniform width flat rim 135 adapted to seat upon the smooth annular flat face 136 formed on ring 1 11. Theaxial dimensions are such that when movable sleeve 122 has been displacedjto the right in FIG. 7 to tightly engage faces 131 and 132, seal ring 134 will be compressed tightly between land 124 and fixed face 136.

Internally, see FIG. 9, a cylindrical pivot pin 140 extends diametrically across movable sleeve 122 with its opposite ends fixed in the sleeve. A connecting rod 141 has its hub 142 rotatably mounted on pm 140 centered axially between fixed space collars 143. An actuating shaft 144, extending from an enclosing housing 77 J similar to that shown-in FIG; 3 and having housing portion 78 welded fluid tight at 145 within a side opening in conduit extension 110, is disposed parallel to pin 140. Crank arms 146 (see FIGS. 8 and 9) are fixedatone end on shaft 144 as by pins 147, and their other ends carry a pivot pin 148 which is pivotally connected to connecting rod 141 to 149.

It will be observed that the bore 151 of hub 142 and the bore 152 of the hubs of levers 146 are of slightly larger diameter than the pivot pins extending through them, thus providing effectively loose pivots. When shaft 144 is rotated, the mechanism 123 is actuated to as disclosed in FIG. 3. Alternatively only one actuator may be used, and one end of shaft 144 merely jourtion along the valve axis by a rear annular land 124 havnalled within the valve assembly.

FIG. 10 disclosed a form similar to FIGS. 6-9 but incorporating two slidable valve sleeves that are actuated in timed relation. In FIG. 10, the movable valve sleeve 122 and all elements at the inlet side of wall 33 are exactly the same as in FIG. 7, and these parts are similarly provide a front seat face such as at 131 and the resilient seal annulus 134 is not needed. This eliminates the need for a rib 133 and seat face 132 in the outlet chamber in FIG. 10.

As shown in FIG. 10, a ring 154 like ring 111 in FIG. 7 is fixed as by welding between shell 22 and the end of sleeve 1 14, and a cylindrical conduit extension 155 like that at 110 in FIG. 7 extends between ring 154 and the outlet conduit. The movable sleeve 153 has at opposite ends cylindrical lands 156 and 157 respectively slidably engaging the cylindrical inner periphery 158 of ring 154 and the cylindrical inner periphery 159 of conduit extension 155.

As shown in FIG. 10, sleeve 153 is displaced longitudinally by an operating mechanism 123 which is the same as that for sleeve 122, and in the assembly the shafts 144 are driven by suitable means (not shown) in such timed relation that during valve closing the inlet port 118 is closed before sleeve 153 closes outlet port 1 19.

Most of the advantages of the form of FIGS. lare equally applicable to these reciprocable sleeve embodiments. The primary distinguishing feature between them is that the rotary sleeve design FIGS. l-5 is mainly intended for flow control only by means of orifice throttlings. It cannot perform as a reliable shut-off valve or isolation device as the FIG. 6-10 form since some leakage will occur in the sleeve clearances. A sleeve valve member slidable along the axis of a ported stationary sleeve can be moved effectively into positive engagement with a pair of annular seats provided interiorly of the valve assembly as disclosed. The movable sleeve 122 is essentially a hollow cylinder having a continuous wall and the valve seats are disposed at the opposite ends of the sleeve when it is moved to the closed position. This arrangement provides for a much tighter seal than can be expected with a rotary sleeve. Such a seal is usually required for an isolation valve, but it is not necessary for a throttle valve.

This valve in FIGS. 6-9 may serve as a single throttle valve by varying the cross-sectional areas of the ports in the stationary sleeve 114 to characterize the openings in much the same fashion as the orifices in FIGS. 1-5. The valve in FIG.v may serve as a 2 stage throttle valve as well as an isolation valve.

Referring to FIG. 11, the stationary sleeve structure surrounded by the annular plenum 161 within shell 22 is of different construction. A cylindrical sleeve section 162 extending within the shell is integral with a ring 163 secured as by welding to the end of inlet conduit 23, and the transverse closure wall 33 is fixed across the inner end of sleeve section 162 which projects slightly beyond wall 33 to provide an axially facing smooth-flat seat 164 lying in a plane normal to the pipe axis. The other sleeve section 165 is rigid with shell 22 and extends within the shell to terminate in an axial flat face 166. The cylindrical outer surface 167 of sleeve section 162 is of slightly less diameter than the cylindrical inner surface 168 of sleeve section 165.

A single movable valve sleeve 171, shown in valve closed condition in FIG. 11, comprises stepped sections 172 and 173 slidable on fixed sleeve sections 162 and 165 respectively.

As shown fixed sleeve section 162 is formed with a series of circumferentially spaced inlet ports 174, and

fixed sleeve section 165 is formed with a series of circumferentially spaced outlet ports 175, the outlet ports preferably being of larger area. Slidable sleeve 171 is formed with a corresponding series of circumferentially spaced ports 176 of a size, number and arrangement corresponding to ports 175.

A resilient seal annulus 177 is mounted in a shoulder 178 on the ring 163 adapted to be engaged and compressed to fluid tight sealing condition when engaged by the flat annular axial end face 179 on sleeve 171 in the closed valve condition, at'which time an annular axially facing seat 181 on sleeve 171 will have engaged seat 164.

A fixed lug 182 stands up from sleeve 171 and a link 183 pivoted to the lug at 184 has a pivot 185 engaged in a slot 186 in a crank arm 187 fixed on the end of an actuating shaft 188. Shaft 188 extends through the shell 22 and is mounted in a seal assembly that is the same as shown in FIG. 3. The foregoing actuating linkage is duplicated at the other side of sleeve 171 in 180 spaced relation to. that illustrated, for balanced operation when the two mechanisms are simultaneously operated.

FIG. 11 shows the parts in valve closed condition. When shaft 188 is rocked counterclockwise, sleeve 171 slides to the right to start gradually uncovering the inlet ports 174. At this point fixed port is. also simultaneously uncovered by port 176 in moving sleeve 171. The combined open port areas at the outlet side are always greater than the uncovered open areas of ports 174 during valve opening.

In all embodiments substantially uniform minimum thickness sleeve and body walls resist thermal shock by avoiding stress concentrations. The structures are relatively easy toanalyze for stresses and this simplifies quality control. The symmetrical ports permit excellent balance of radial flow forces, and axial forces are nearly balanced in all embodiments. Several of the foregoing assemblies may be used in series in a pipe line for further multi-stage control.

The invention maybe embodied in other specific forms without departing from the spirit or essential characteristics thereof. The present embodiments are therefore to be considered in all respects as illustrative and not restrictive, the scope of the invention being indicated by the appended claims rather than by the foregoing description, and all changes which come within the meaning and range of equivalency of the claims are therefore intended to be embraced therein.

What is claimed and desired to be secured by Letters Patent is:

1. In a valve assembly for controlling flow of high temperature fluid a valve body having internal means defining longitudinally separate inlet and outlet chambers surrounded by an annular plenum chamber, fixed port means providing fluid communication between the plenum chamber'and the respective inlet and outlet chambers, movable valve means shiftable for controlling fluid flow through said chambers, means for displacing said movable valve means comprising an actuating shaft projecting into said valve body into the path of hot fluid flowing through said valve assembly where linkage connects said shaft to said movable valve means, housing means secured to said valve body and sealingly surrounding the shaft externally of said valve body, and means for continually extracting heat from said housing means for localized cooling of hot fluid that may have entered said housing means along the shaft comprising an external highly heat conductive metallic mass secured to saidhousing means and a plurality of heat radiating fins on said mass.

2. In a valve assembly, a body having internal means defining longitudinally separate inlet and outlet chambers surrounded-by an annular plenum chamber, fixed port means providing fluid communication between the plenum chamber and the respective inlet and outlet chambers, movable valve means shiftable for controlling fluid flow through said chambers comprising at least one. sleeve movably mounted for displacementinto covering and uncovering relation with respect to comprising a rotatable shaft projecting into said plenum chamber where linkage connects it to said movable valve means, and means for blocking external transfer of heat along said shaft.

3. Ina valve assembly, a body having internal means [defining longitudinally separate inlet and outlet chambers surrounded by an annular plenum chamber, fixed port means providing fluid communication between the plenumchamber. and the respective inlet and outlet chambers, movable valve means shiftable for controlling fluid flow through said chambers comprising a rotary ported sleeve, and diametrically opposite actuating mechanisms for rotating said sleeve mounted in said plenum chamber. Y

4. In a valve assembly, a body having internal means defining longitudinally separate inlet and outlet chambers surrounded by an annular plenum chamber, fixed port means providing fluid communication between the plenum chamber and the respective inlet and outlet chambers, and movable valve means shiftable for controlling fluid flow through said chambers comprising two longitudinally shiftable sleeves operated in timed relation. 9

said port means, means for actuating said valve means said shaft and the component of said valve assembly through which said shaft extends, said movable valve 5. ,In a high temperature valve'assembly wherein a I movable valve member is enclosed within a valve body for controlling flow of a hot fluid metal having a melting point appreciably below' that of the metal of said valvemember and body, a rotatable actuating shaft operably connected to said valve member and projecting out of said body, housing means enclosing the shaft outside the body, and means for continuously extracting heat from said housing for solidifying molten metal that may enter the space between said housing and shaft comprising a body of highly heat conductive material secured upon said housing for localized concentrated transfer of heat to the body and a plurality of heat radiating fins mounted to dissipate heat transferred to said body.

plenum chamber and the respective inlet and outlet chainbers, movable valve meansshiftable for con troll ng fluid flow through said chambers, means for uc-' tuating said movable valve means. comprising a, shaft projecting into the path of fluid flowingthrough said valve assemblyv where linkage connects said shaftto said movable valve means, and sealing' means between said shaft and the component of said valveassembly through which said shaft extends, said internal means comprising a fixed sleeve internally closed; by a transverse wall, and said fixed port means comprising at one side of said wall at least one port in the sleeve wall connecting the inlet and plenum chambers and at the other side of said wall at least one port in the sleeve wall con-' necting the outlet and plenum chambers.

9. In a valve assembly, a body having-internal means defining longitudinally separate inlet and outlet chambers surrounded by an annular plenum chamber, fixed port means providing fluid communication between the plenum chamber and the respective inlet and outlet chambers, movable valve means shiftable for controlling fluid flow through said chambers, means for actuating said movable valve means-comprising a shaft projecting into the path of fluid flowing through said valve assembly where linkage connects said shaft to said movable valve means, and sealing means between means comprising at least one sleeve movably mounted for displacement into covering and uncovering relation with respect to said port means,

10. In the valve assembly defined in claim 9, said movable sleeve being rotatably mounted.

11. In the valve assembly defined in claim 9, said movable valve assembly being longitudinally slidably mounted. v .f,

12. In the valve assembly defined in claim 9, said wall being concave facing said inlet. a

13. In a valve assembly, -a body having internal means defining longitudinally separate inlet and outlet chambers surrounded by an annularplenum chamber, fixed port means providing fluid communication between the plenum chamber and the respective inlet and outlet 6. In the valve assembly defined in claim 5, said heat chambers, movable valve means shiftable for controlling fluid flow through said chambers, means for actuating said movable valve means comprising a shaft projecting intov the path of fluid flowing through said valve assembly where linkage connects said shaft to said movable valve means, and sealing means between said shaft and the component of said valve assembly I through which said shaft extends, saidintemal means comprising a fixed sleeve having an internal wall separating it into said inlet and outlet chambers, said plenum chamber surrounding said fixed sleeve, and said sleeve being laterally ported at both the inlet and outlet sides of said internal wall.

14. In the valve assembly defined in claim 13, said movable valve means comprising a ported sleeve rotatably mounted on said fixed sleeve.

15. In the valve assembly defined in claim 13, said movable valve means comprising a sleeve slidable longitudinally along said fixed sleeve. 

1. In a valve assembly for controlling flow of high temperature fluid a valve body having internal means defining longitudinally separate inlet and outlet chambers surrounded by an annular plenum chamber, fixed port means providing fluid communication between the plenum chamber and the respective inlet and outlet chambers, movable valve means shiftable for controlling fluid flow through said chambers, means for displacing said movable valve means comprising an actuating shaft projecting into said valve body into the path of hot fluid flowing through said valve assembly where linkage connects said shaft to said movable valve means, housing means secured to said valve body and sealingly surrounding the shaft externally of said valve body, and means for continually extracting heat from said housing means for localized cooling of hot fluid that may have entered said housing means along the shaft comprising an external highly heat conductive metallic mass secured to said housing means and a plurality of heat radiating fins on said mass.
 2. In a valve assembly, a body having internal means defining longitudinally separate inlet and outlet chambers surrounded by an annular plenum chamber, fixed port means providing fluid communication between the plenum chamber and the respective inlet and outlet chambers, movable valve means shiftable for controlling fluid flow through said chambers comprising at least one sleeve movably mounted for displacement into covering and uncovering relation with respect to said port means, means for actuating said valve means comprising a rotatable shaft projecting into said plenum chamber where linkage connects it to said movable valve means, and means for blocking external transfer of heat along said shaft.
 3. In a valve assembly, a body having internal means defining longitudinally separate inlet and outlet chambers surrounded by an annular plenum chamber, fixed port means providing fluid communication between the plenum chamber and the respective inlet and outlet chambers, movable valve means shiftable for controlling fluid flow through said chambers comprising a rotary ported sleeve, and diametrically opposite actuating mechanisms for rotating said sleeve mounted in said plenum chamber.
 4. In a valve assembly, a body having internal means defining longitudinally separate inlet and outlet chambers surrounded by an annular plenum chamber, fixed port means providing fluid communication between the plenum chamber and the respective inlet and outlet chambers, and movable valve means shiftable for controlling fluid flow through said chambers comprising two longitudinally shiftable sleeves operated in timed relation.
 5. In a high temperature valve assembly wherein a movable valve member is enclosed within a valve body for controlling flow of a hot fluid metal having a melting point appreciably below that of the metal of said valve member and body, a rotatable actuating shaft operably connected to said valve member and projecting out of said body, housing means enclosing the shaft outside the body, and means for continuously extracting heat from said housing for solidifying molten metal that may enter the space between said housing and shaft comprising a body of highly heat conductive material secured upon said housing for localized concentrated transfer of heat to the body and a plurality of heat radiating fins mounted to dissipate heat transferred to said body.
 6. In the valve assembly defined in claim 5, said heat extracting means being a relatively thick metal annulus that is axially short as compared to the length of the housing upon which it is secured.
 7. In the valve assembly defined in claim 6, said housing being of ferrous metal and said annulus being composed of copper or another metal or alloy having a higher coefficient of heat transfer than the housing metal.
 8. In a valve assembly, a body having internal means defining longitudinally separate inlet and outlet chambers surrounded by an annular plenum chamber, fixed port means providing fluid communication between the plenum chamber and the respective inlet and outlet chambers, movable valve means shiftable for controlling fluid flow through said chambers, means for actuating said movable valve means comprising a shaft projecting into the path of fluid flowing through said valve assembly where linkage connects said shaft to said movable valve means, and sealing means between said shaft and the component of said valve assembly through which said shaft extends, said internal means comprising a fixed sleeve internally closed by a transverse wall, and said fixed port means comprising at one side of said wall at least one port in the sleeve wall connecting the inlet and plenum chambers and at the other side of said wall at least one port in the sleeve wall connecting the outlet and plenum chambers.
 9. In a valve assembly, a body having internal means defining longitudinally separate inlet and outlet chambers surrounded by an annular plenum chamber, fixed port means providing fluid communication between the plenum chamber and the respective inlet and outlet chambers, movable valve means shiftable for controlling fluid flow through said chambers, means for actuating said movable valve means comprising a shaft projecting into the path of fluid flowing through said valve assembly where linkage connects said shaft to said movable valve means, and sealing means between said shaft and the component of said valve assembly through which said shaft extends, said movable valve means comprising at least one sleeve movably mounted for displacement into covering and uncovering relation with respect to said port means.
 10. In the valve assembly defined in claim 9, said movable sleeve being rotatably mounted.
 11. In the valve assembly defined in claim 9, said movable valve assembly being longitudinally slidably mounted.
 12. In the valve assembly defined in claim 9, said wall being concave facing said inlet.
 13. In a valve assembly, a body having internal means defining longitudinally separate inlet and outlet chambers surrounded by an annular plenum chamber, fixed port means providing fluid communicaTion between the plenum chamber and the respective inlet and outlet chambers, movable valve means shiftable for controlling fluid flow through said chambers, means for actuating said movable valve means comprising a shaft projecting into the path of fluid flowing through said valve assembly where linkage connects said shaft to said movable valve means, and sealing means between said shaft and the component of said valve assembly through which said shaft extends, said internal means comprising a fixed sleeve having an internal wall separating it into said inlet and outlet chambers, said plenum chamber surrounding said fixed sleeve, and said sleeve being laterally ported at both the inlet and outlet sides of said internal wall.
 14. In the valve assembly defined in claim 13, said movable valve means comprising a ported sleeve rotatably mounted on said fixed sleeve.
 15. In the valve assembly defined in claim 13, said movable valve means comprising a sleeve slidable longitudinally along said fixed sleeve. 